Variable gearing



Dec. 10, 1935. c. K. SCHWARTZ VARIABLE GEARING 6 Sheets-Sheet 1 Original Filed July 7, 1953 FIG? 6.

INVENTOR CABL A. Scunmerg,

ATTO RN EY Dec. 10, 1935. c. K. SCHWARTZ VARIABLE GEARING Original Filed July 7, 1933 6 Sheets-Sheet 2 INVENTOR C224 A. SCHWABTZ,

MAMA

ATTORNEY Dec. 10;. 1935. c sc w -z 2,024,115

VARIABLE GEARING Original-Filed July '7, 1933 6 Sheets-Sheet 4 INVENTOR CABL K SCHWAfiTZ, BY I I A-TTORNEY v Dec. 10, 1935.

c. K. SCHWARTZ 2,024,115

VARIABLE GEARING Original Filed July' 7, 1933 v 6 Sheets-Sheet 5 INVENTOR v 6142/. /1. ScHwAerz, BY @TORNEY Dec. 10, 1935. G K, CHWARTZ 2,024,115

VARIABLE GEARING Original Filed July '7, 1933 6 Sheets-Sheet 6 rlll'lllllllllllallnll INVENTOR CARL A. Scum A277 ATTORNEY Patented Dec. 10, 1935 UNITED STATES PATENT OFFICE John Wood Manufacturing Company, Inc.,

Conshohocken, Pa., a. corporation of Delaware Original application July 7, 1933, Serial No.

679,292. 1934, Serial No. 727,229

12 Claims.

This is a division ,of my original application erial No. 679,292 filed July '7, 1933, for Letters Patent of the United States for improvement in liquid dispensing apparatus wherein the claims are drawn to dispensing and registering apparatus. The claims in this case are drawn to the variable gearing and auxiliary variable drive con-- nection which are particularly applicable to coopcratively connect the meter of a liquid dispensing mechanism with means for computing and registering the value of the liquid dispensed in accordance with the price per unit of volume for which the mechanism may be variably manually set.

My invention is particularly applicable to metering pumps for dispensing gasolene. The principal object and effect thereof is to provide simple and efficient means for automatically computing and visibly displaying, by registering mechanism, the value of the liquid dispensed at each transaction, in acordance with the volume of liquid thus dispensed. Such computation may be based upon any predetermined price of the liquid per unit of volume, which price may be varied, in fractions, of a cent, by manually adjusting the computing mechanism.

In the form of my invention illustrated, the unit of gasolene is a gallon, and its value computed in tenths of a cent. The value based upon the whole cents of the price, and the value based upon any fraction of a cent of the price, are respectively computed by a main mechanism and an auxiliary mechanism, but they are in such cooperative relation that the result of the auxiliary computation is automatically added to the result of the main computation and the aggregate value thereof automatically displayed by the registering mechanism.

My invention includes the various novel features of construction and arrangement hereinafter more definitely specified.

Fig. 1 is a view partly in elevation and partly in sectionof a gasolene dispensing apparatus of the curb stand type equipped with this invention.

Fig. 2 is a vertical sectional view of the computing and registering mechanism taken substantially on the line 2-2 in Fig. 1.

Fig. 3 is a fragmentary vertical sectional view taken on the line 33 in Fig. 2. i

Fig. i is an enlarged view similar to Fig. 2, but illustrating only the driving connections of the computing mechanism.

5 is an enlarged inverted plan View of a portion of the mechanism shown in Fig. 2, illus- Divided and this application May 24,

trating particularly the driving means for the computing and registering mechanism.

Fig. 6 is a fragmentary vertical sectional view taken on the line 6-6 in Fig. 2.

Fig. 7 is a partly sectional elevation showing 5 the connection between the main and auxiliary driving means, for the computing mechanisms, taken on the line 'l-'| in Fig. 2.

Fig. 8 is a vertical longitudinal sectional view of the structure shown in Fig. '7, the parts being separated.

. Fig. 9 is a perspective view of the pawl, which forms part of the connection shown in Figs. 7 and 8.

Fig. 10 is a vertical sectional view, taken on m the line Iii-40 in Fig. 2; showing an elevation of two of the dials of the registering mechanism indicated in Fig. 1.

Fig. 11 is an enlarged fragmentary partly sectional perspective view of the driving connection between the main and auxiliary computing means.

Fig. 12 is a fragmentary plan sectional view showing the frictional driving connection between the indicator shaft, of the registering mechanism, and the gear for driving it, taken on the line l2--l2 in Fig. 2; and

Fig. 13 is a vertical sectional view taken on the line l3-l3 in Fig. 2.

Referring to Fig. 1: The casing 5 is mounted on a suitable base 6 and contains a pump 1 driven by an electric motor 8. The inlet of the pump is connected through a pipe 9 with a source of gasolene supply, usually an underground tank (not shown) and the outlet of the pump is connected through a pipe I 0 with a meter ii. The outlet of the meter l I is connected through a. pipe l2, with a dispensing hose l3, the free end of which has a discharge nozzle [4 provided with a normally closed valve I5.

As is customary, the discharge nozzle, when not in use, is supported on a movable hook l6 projected from the side of the casing, the weight of the nozzle being suflicient to hold the hook down. Upon removal of the discharge nozzle from the hook IS, the hook rises to close a motor starting switch which starts the pumping action. However, no liquid is discharged from the nozzle until the valve l5 therein is opened, this being controlled by a handle l1.

As the liquid is dispensed from the nozzle, an impeller or other suitable rotatable means (not shown) forming part of the meter structure ll, imparts rotation to a power take-off shaft l8 through a gear connection indicated as at I9.

This power take-01f shaft I8 is ordinarily utilized to drive an amount registering pointer or similar indicating means, but in the present in stance, it is utilized to drive and actuate the cost computing mechanism indicated generally by the numeral 20.

The cost registering or indicating mechanism includes a pair of spaced dials 2i visible through glass panels 22 on two opposite sides of the dispensing apparatus; these dials are divided into one hundred equal spaces with graduations corresponding to one cent divisions, as best shown in Fig. 10, and cooperable with each is an indicator pointer 23 rotatable about the face of the dial.

Coacting with the dials 2i are smaller dollar indicating dials 24, the upper portions of which are visible above the dials 2!. These dollar indicating dials are graduated and coact with a fixed pointer 25 to indicate whole dollars and in conjunction with the pointers 23 and the dials 2i,

designate the total cost of the liquid dispensed.-

The dollar indicating dials 24 are fixed to a common sleeve 26 rotatably mounted on a sleeve 2'] forming a tie between the stationary dials 20. A gear 28 fixed to the sleeve 26 and meshing with a pinion 29, which is mounted on a shaft 30 carrying the pointers 23, provides a driving connection from the shaft 30 to the dials 24, this gear and pinion connection being of such ratio that the dials 24 are moved the angular distance from one graduation to the next during the complete rotation of the pointers 23. In this manner, the conjoint use of the two dials enables the registration of the cost of any normal or usual amount of gasoiene dispensed.

As stated, the two stationary dials 2B are rigidly connected by the sleeve 21. A pair of tie rods Si at opposite sides of the central axis of the dials cooperate with the sleeve 2? to securely connect the dials in rigid spaced relation. These tie rods 35 extend along opposite sides of the driving mechanism indicated generally by the numeral 82 and are attached thereto to receive support as will be presently described.

The driving mechanism indicated generally by the numeral 32, is assembled on a frame consisting of two spaced parallel end plates 33 and 3d rigidly connected by two upper rods 55 and two lower rods 36. The lower rods 36 rest on a support 3'! carried by the top of the meter ii and are clamped down on said support by a cross piece 33.

Extending transversely across the two rods ill connecting the dials and the upper rods 35 is a clamping structure 39 by which the rods 38 and the dials attached thereto are supported from the driving mechanism and, as the driving mechanism is in turn supported from the meter, the entire registering apparatus receives its support from the meter. This is a particularly advantageous manner of mounting the mechanism as it insures alignment with the power take-off shaft 88. Said shaft i3 is used to drive the shaft 30 carrying the pointers 23 and also to drive the dials 2 3 as follows:

A shaft 46 journaled in a bearing ll fixed to the end plate 33 and having a bevel gear 32 at its upper end and the cross pin 43 at its lower end, is directly driven from the shaft i8 through the driving connection afforded by the engagement of the shaft cross pin "33 in a cross slot 44 in the end of the shaft I8. The shaft 50 and its bevel gear 42 thus are driven from the impeller of the meter in predetermined fixed ratio to the amount of liquid dispensed.

The bevel gear 42 meshes with a gear 55 fixed to a shaft 46 journalled at one end in a bearing 41 carried by the end wall 34 and at its opposite end in a bearing 48 carried by an outer supporting wall 49. The wall 49 is supported from the end wall 33 by a pair of studs 50. shown in Fig. 4, the end wall 33 is apertured as at i to accommodate the gear 45.

Mounted on the shaft 46 between the end walls 33 and 34 is a group of twenty-one driving gears 52, ranging in size from ten to thirty teeth, each being one tooth larger than the preceding gear. Also secured to the shaft d6 between the gear &5 and the outer supporting wall $9 is a plurality of driving cams 53, there being ten cams having progressively increasing numbers of high spots substantially in the form of teeth 54 ranging from no teeth on the cam closest the gear 45 to nine teeth on the cam at the opposite end of the series. The purpose of these cams is to actuate an auxiliary driving connection which is supplemental to that afforded by the group of gears 52, as will be hereinafter more fully described.

Above the shaft 56 is a gear shaft 55 journaled in bearings 56 and 57 carried respectively by the end walls 33 and 3B. This shaft has ten gear teeth out into it which extend throughout its entire length, and has a sleeve 58 slidably and freely rotatably mounted thereon. The sleeve 58 has an arm 5% projecting therefrom, the outer end of whichis slotted as at 50. Adjustably secured in the slot 50 is a bearing stud 56 for a large idler gear 52, which is freely rotatable on its bearing stud 6 i, and is at all times in mesh with the teeth of the shaft 55, the adjustment aiforded by the slot 50 enabling the gear to be properly meshed with the teeth of the shaft 55. As best shown in Fig. 3, the gear 62 extends through the side of the sleeve 58, for its engagement with the teeth of the shaft 55;

In this manner, the idler gear 52 is at all times in mesh with the shaft 55, regardless of its location with respect to the length of the shaft 55, so that the idler gear 62 may be engaged with any one of the group of driving gears 52 to establish a driving connection between the shafts 6 and 55. The ratio of the drive between the shafts t6 and 55 is of course determined by the selection of the gear in the group 52.

To hold the sleeve 58 carrying the idler gear in an adjusted position and to facilitate the selection of the proper gear52, a scale 63 is provided. The scale 63 consists of a flat metal bar depending from a stud 54 and having a plurality of comb teeth t5 defining spaces with which a fiat web 636 carried by the supporting sleeve 58 is engageable.

The location of the spaces between the comb teeth 65, and the web 66 with respect to the idler gear 62 is such that by engaging the web $8 in the first space at the left hand end of the scale with respect to Figs. 2 and i, the idler gear will be meshed with the smallest of the group of gears 52. The successive spaces correspond to the successive gears in the group 52 and as the gears in the group range from ten to thirty teeth inclusive and the shaft 55 also has ten teeth, the ratio obtained by the engagement of the idler with the first or smallest gear of the group 52, will he one to one, representing in the present instance, a unit cost per unit of measure of the 70 liquid of ten cents. This amount is delineated on the scale 53 opposite the first space as clearly As clearly 5 the spaces between the comb teeth 65. The manner of effecting this disengagement is clearly illustrated indotted lines in Fig. 3'.

Said idler 62 and the elements cooperative therewith, as specified, constitute means for manually adjustably varying the ratio of the main driving connection between the driving member of the meter II which actuates the shaft 40 of the computing mechanism, and the registering indicating mechanism" comprising the rotary pointers 23 and the rotary dials 24.

Mountedon the end of the gear shaft adjacent the wall 33 is a ratchet driving connection indicated generally by the numeral 61 through which rotation of the shaft 55 is imparted to a pinion 68 which meshes with a gear 69 connected through a yielding clutch 10 illustrated in detail in Fig. 12 to drive the shaft 30 on which the indicator pointers 23 are mounted.

The ratchet driving conn'ection'GI adds the computing result of the driving action of the auxiliary drive obtained through the action of the cams 53 in a manner to be hereinafter described, to the computing result of the driving action afforded by the main driving connection which is through, the group of gears and the idler 62.

Referring to Figs. '7, 8, 9, 11, and 13: The ratchet connection includes a flanged disk or cup H fixed on the gear shaft 55 to form a driving member, and a driven member provided by a ratchet wheel I2 secured to a shaft I3 on the outer end of which the pinion 68 is cut. The inner end of the shaft I3 is bored as at 14 to be journaled on the end I5 of the shaft 55. This end of the shaft 55 is drilled to form a spring pocket I6 in which the compressible spring 11 is received, the outer end thereof bearing against the bottom of the bore 14 and yieldably urging the stub shaft I3 and consequently the ratchet wheel I2 outwardly of the flanged disk or cup II. The thickness of the ratchet wheel I2 is less than the depth of the flange of the cup so that a limited degree of axial movement is permitted the ratchet wheel, without necessitating projection of the wheel beyond the outer edge of the flange.

After being assembled with the cup 1| the head of a screw I8 threaded in the flange of the cup and overlying the ratchet wheel, as shown in Fig. 7, prevents separation of these elements under action of the spring 11.

As shown in Figs. 7 and 8: At diametrically opposite portions the flange of the cup is slotted as at I9. In one of these slots 19 is a spring pawl 80 rigidly mounted at its outer end and adapted to engage the teeth of the ratchet wheel I2 to provide a uni-directional driving connection between the cup and the ratchet wheel, the position of the spring pawl being such that the ratchet wheel and consequently the pinion 58 are driven in the proper direction by rotation of the shaft 55 through the idler 62. It is to be noted that the spring pawl is wide enough to maintain engagement with the ratchet wheel regardless of the axial shifting of the ratchet wheel in the In the opposite slot 19 is a second pawl 8| pivotally mounted and spring pressed by a flat leaf spring 82 into engagement with the teeth of the ratchet wheel. The free end of the pawl is formed with an inclined edge 83, as shown in Fig. 9, which engages the teeth of the ratchet wheel. The angle of this inclined edge and the location of the pawl with respect to the possible endwise or axial movement of the ratchet wheel I2 is such that upon inward shifting of the ratchet wheel, the action of the inclined edge advances the ratchet wheel the distance of one tooth. It is thus through an endwise shifting of the ratchet wheel 12 that the supplemental driving action 5 and auxiliary computation is effected.

It is to be noted that the location of the pawl 8| with respect to the range of possible endwise movement of the ratchet wheel I2 is such that at no time will the ratchet wheel be disengaged 10 from the pawl. As the wheel is moved outwardly by the spring II, the pawl snaps past one tooth and engages the next one so that upon the following inward movement, the ratchet wheel is advanced the distance of one tooth. is

So as not to disrupt the driving connection between the pinion 68 and the gear 69, the pinion is of suflicient length to permit its axial reciprocation while in mesh with the gear 69.

The axial reciprocation of the shaft I3 and con- 20 sequently the ratchet wheel I2, is effected through the operation of the cams 53 in the following manner: Frictionally slidable and journaled for oscillation on one of the studs 50, as shown in Figs. 4 and 6, is a cam follower in the form of a-25 finger 84, the outer end of which is adapted to overlie and ride any one of the series of cams 53. Said finger 84 is manually axially adjustable on its stud 50 to selectively register with any one of said cams 53 and is held in its adjusted posi- 30 tion by its frictional engagement with said stud. I Said cam follower or finger 84 and the elements of the mechanism with which it cooperates, as described, constitute means for manually adjustably varying the ratio of the auxiliary driving 35. connection between the driving member of the meter I I which actuates the shaft 40 of the computing mechanism, and the registering indicating mechanism comprising the rotary pointers 23 and the rotary dials 24. Also mounted for oscilla- 40 tion on the same stud 50 but restrained against axial sliding movement thereon, by selective manual engagement in the spaces between said cams 53, as indicated in Figs. 1, 2, and 4, is a. lifting finger 35, the outer end of which bears against 45 the short arm of a bell crank lever 85 fulcrumed on the pin 81 between bracket plates 88 carried by the outer support 49. The outer end 89 of the long arm of the bell crank lever bears against the adjacent end of the shaft I3 whereby lifting 50 of the finger 85 moves the shaft 13inwardly.

As shown in Fig. 6, said cam follower 84 is also mounted to slide axially on the rod 90 which is rigidly connected at its outer end with said lifting flnger 85 so that lifting movement imparted 55 to said cam follower 84 by any cam 53 with which said follower is selectively engaged is imparted to said lifting finger 85. l i

If the cam follower is aligned with the cam at the extreme left of the series, with respect 1:0 Figs. 2 and 4, this cam having no depressions or high spots, will impart no movement to the follower.

The next successive cam, however, will import one lifting action for each complete revolution 55 of the shaft 46. This cam corresponds to onetenth of a cent and through the advancing of the ratchet wheel affected by its endwise shifting in the manner hereinbefore described, it advances the ratchet wheel one tooth for each complate revolution of the shaft 46. The teeth of the ratchet wheel being one hundred in number correspond to tenths of a cent. The advance of the ratchet wheel and consequently the indicator pointers 23 obtained in this manner augments the drive of the gear (59 and the. indicator point ers 23 through the main driving connection. That is to say; the result of the auxiliary computation eifected with reference to tenths of one cent by movement of said ratchet wheel i2 is merely added to the result of the main computation based upon whole cents of the price of the liquid dispensed; so that the aggregate Value of the two computations is manifested by said pointers 23.

The cams 53, as hereinbefore noted, range in the number of their projections 54 from zero on the left to nine at the right end of the series. To facilitate the adjustment of the cam follower, a scale Qi is provided. This scale may be of any desired design and construction and in the present instance is shown merely as a fiat strip of metal secured to the end support M3 and suitably graduated and numerically marked.

The yieldable clutch it between the driving gear 69 and the shaft 36, as illustrated in Fig. 12, consists merely of a flat spring t2 disposed in a groove 93 cut into the shaft 3t and bearing against the inner face of the bore in a sleeve hub 9 fixed in the gear 68.

The clutch it affords a frictional connection between the gear 69 and the shaft 30 sufficient to drive the indicator pointers 23 and the dials 24 and at the same time yields to permit forced turning of the indicator pointers 23 by means of knobs 95 provided for this purpose. This is necessary as the indicator pointers and the dials 24* must be brought to their zero positions before beginning each dispensing operation.

Said mechanism operates as follows: Assuming that the unit cost per unit of measure of the gasolene to be dispensed is twenty-three and fivetenths cents, the idler gear 62 is meshed with .in Fig. 4.

Inasmuch as the gear with which the idler S2 meshes has twenty-three teeth, the shaft 55 and the pinion 68 each have ten teeth, and the gear 69 has one hundred teeth, the ratio of the main driving connection between the shaft 46 and the shaft 55 is twenty-three to ten, so that upon each complete revolution of the shaft it, the shaft 55 will turn two and three-tenths revolutions, causing the gearGQ to turn twenty-three one hundredths of a complete turn.

Simultaneously with this driving action, the pinion 68 will be advanced a distance equal to five teeth on the ratchet wheel 712, which moves the gear 69 and the pointer shaft 393 half the angular distance of one graduation. Hence, the pointers will indicate a cost of twenty-three and one-half cents, or the cost of one gallon of gasolene, the dispensing of one gallon turning the power takeoff shaft [8 and consequently the shaft in, one revolution.

The pointers 23 thus turn quit/e slowly. This fact is particularly an advantage as it insures greater accuracy where it is desired to dispense only a predetermined amount of gasolene.

It is, of course, understood that access may be had tothe mechanism only by those authorized, through a locked door in the casing of the dispensing apparatus, so that the adjustment of the unit cost per unit of measure cannot be tampered with.

However, I do not desire to limit myself to the precise details of construction and arrangement aoaans herein set forth as it is obvious that various modifications may be made therein without departing from the essential features of my invention, as defined in the appended claims.

I claim:

1. In combination with a driving member and a driven member, ratchet means forming. a driving connection between said members, said ratchet means including a ratchet wheel and a pawl axially movable with respect to each other, means 10 to effect relative axial movement between the ratchet wheel and pawl while retaining the driving engagement therebetween, and means operable upon said relative axial movement of the wheel and pawl to advance the driven member with respect to the driving member and thus augment its actuation by the driving member.

2. In combination with a driving member and a driven member, ratchet means forming a driving connection between said members, said ratchet means including a ratchet wheel and a pawl axially movable with respect to each other, means to eifect relative axial movement between the ratchet wheel and pawl while retaining the driving engagement therebetween, and a member having an inclined portion engageable with the teeth of the ratchet wheel and operable upon said relative axial movement of the wheel and pawl to advance the driven member with respect to the driving member and thus augment its actuation by the driving member.

3. In combination with driving and driven members, means forming a driving connection between said members comprising, a ratchet wheel rigidly connected to one of said members, means carried by the other of said members to engage the teeth of the ratchet wheel and form a driving connection accommodating endwise motion between said ratchet wheel and said means while at all times maintaining the driving con- 40' nection afforded thereby, and means operable upon endwise relative movement between said ratchet wheel and said means to advance the ratchet wheel and thus augment the driving action of the driving member. 4. In anapparatus of the character described, a driving member, a driven member, means to drivingly connect said members including a ratchet wheel carried by one of said members and an element carried by the other of said members and engaging the teeth of the ratchet wheel,

said members being arranged for relative endwise motion while retaining the driving connection provided by said element engaging the teeth of the ratchet wheel, and a pawl having an inclined edge engaging the teeth of the ratchet wheel, said pawl being arranged so that endwise relative motion between said members also effects endwise shifting between the ratchet wheel and the pawl and said inclined edge of the pawl advancing the ratchet wheel during such relative endwise motion.

5. In an apparatus of the character described, a driving member, a driven member, means to establish a driving connection between said members comprising a ratchet wheel mounted on the driven member, a pawl carrier attached to the driving member, pawl means on said carrier engageable with the teeth of the ratchet wheel, said members being adapted for endwise relative motion while retaining the driving engagement of said pawl means with the teeth of the ratchet wheel, means to periodically eifect endwisemotion between said members, and a member on said pawl carrier 'engageable with the teeth of the ratchet wheel to advance the ratchet wheel upon such endwise relative motion of said members.

6. In an apparatus of the character described, a driving shaft, a driven shaft in axial alignment therewith and adapted for relative axial motion with respect thereto, a ratchet wheel on one of said shafts, a pawl carrier on the other of said shafts, pawl means on said carrier engaging the teeth of the ratchet wheel to form a driving connection between said shafts, the engagement of said pawl means with the ratchet wheel accommodating endwise relative motion of said shafts, and a second pawl means on said carrier and engageable with the teeth of the ratchet wheel, said second pawl means having an inclined ratchet wheel engaging edge adapted upon endwise shifting of said shaft to" advance the driven shaft and thus augment the driving action of the driving shaft.

'7. In apparatus of the character described, a driving shaft, a driven shaft in axial alignment therewith, a ratchet wheel on the driven shaft, a cup on the driving shaft to receive the ratchet wheel, the driven shaft with the ratchet wheel thereon being shiftable endwise with respect to the driving shaft and the cup, means to yieldably urge the driven shaft and the ratchet wheel away from the driving shaft and cup, pawl means carried by the cup and engaging the teeth of the ratchet wheel to establish a driving connection between said shafts which connection is maintained during endwise relative motion, a second pawl means carried by the cup and engaging the teeth of the ratchet wheel, said second pawl means having an inclined tooth engaging portion adapted upon endwise relative motion of the ratchet wheel to advance the ratchet wheel and the driven member and thus augment the driving connection of the first pawl means with the ratchet wheel, and means to periodically move the driven member and the ratchet wheel toward the driving shaft and cup against the action of said spring means.

8. An apparatus of the character described, comprising a driving shaft, a driven shaft in axial alignment with the driving shaft and freely r0- tatable and endwise shiftable with respect to the driving shaft, one of said shafts having its end piloted in a bore in the other shaft, spring means between the shafts to yieldably urge the same apart, a ratchet wheel fixed to the driven shaft, a housing member fixed to the driving shaft and arranged to receive the ratchet wheel, said housing being of greater depth than the width of the ratchet wheel so that the driven shaft with the ratchet wheel has a degree of. relative axial shifting movement with respect to the housing without necessitating removal of the ratchet wheel from the housing, pawl means carried by the housing and engaging the teeth of the ratchet wheel to provide a driving connection between said shafts which connection is maintained regardless of endwise relative motion between the shafts, and a second pawl means carried by the housing and having an inclined edge engaging the teeth of the ratchet wheel during endwise relative motion of said shafts, and means to periodically push the driven shaft toward the driving shaft against the action of said spring means to effect such relative endwise motion.

9. In an apparatus of the character described,

a drive shaft, a member to be driven from said shaft, a bank of progressively larger gears fixed to said drive shaft, a plurality of different cams fixed to said drive shaft, gear means selectively 5 engageable with one of the gears of said bank to provide a driving connection between said drive shaft and the member to be driven, and means operable by a selected cam to supplement the driving action of said gear means.

10. In apparatus of the character described, a rotatable drive shaft, a shaft to be driven from the drive shaft, an intermediate shaft, a bank of different diameter gears on the drive shaft, a series of cams having progressively increasing numbers of high and low points also mounted on the drive shaft, gear meansat all times drivingly connected with the intermediate shaft and selectively engageable with any gear of said bank of gears to establish a driving connection between the drive shaft and the intermediate shaft, a clutch connection between the intermediate shaft and the shaft to be driven, whereby the shaft to be driven is actuated from the intermediate shaft and whereby the shaft to be driven is free to advance ahead of the intermediate shaft, and means operable by a selected cam to advance the shaft to be driven ahead of the intermediate shaft without disturbing the driving action of the intermediate shaft,

11. In apparatus of the character described, a drive shaft, a shaft to be driven, an intermediate shaft substantially in axial alignment with the shaft to be driven, said shaft to be driven and the intermediate shaft being adapted for endwise relative motion, a ratchet driving connection between the intermediate shaft and the shaft to be driven including means operable upon relative endwise motion of said shafts to advance the shaft to be driven with respect to the intermediate shaft, a series of different diameter gears carried by the drive shaft, a series of cams having progressively increasing numbers of high and low spots also carried by said drive shaft, gear means at all times in driving connection with the intermediate shaft and selectively engageable with any gear of said series to afford a driving connection between the drive shaft and the intermediate shaft, and means operable by any selected cam to periodically effect relative endwise motion between the shaft to be driven and the intermediate shaft and thereby advance the shaft to be driven without disturbing the driving action afforded by the gear means.

12. In a mechanical movement embodying ,55 compound variable drive mechanisms; a ratchet wheel; and means for imparting'to said ratchet wheel axial movement and consequent rotary movement, and other means for imparting rotary movement to said wheel independently of such 0 CARL K. SCHWARTZ. 7 

